JP7286645B2 - capacity control valve - Google Patents

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a displacement control valve that variably controls the displacement of a working fluid, and for example, to a displacement control valve that controls the discharge amount of a variable displacement compressor used in an automotive air conditioning system according to pressure.

A variable displacement compressor used in the air conditioning system of automobiles consists of a rotating shaft driven by the engine, a swash plate connected to the rotating shaft so that the angle of inclination can be changed, and a compression piston connected to the swash plate. etc., and by changing the inclination angle of the swash plate, the stroke amount of the piston is changed to control the discharge amount of the fluid. The inclination angle of the swash plate is determined by using a displacement control valve that is driven to open and close by electromagnetic force. By appropriately controlling the pressure in the control chamber while utilizing the control pressure Pc in the control chamber containing the swash plate, the pressure can be changed continuously.

During continuous operation of the variable displacement compressor (hereinafter sometimes simply referred to as “during continuous operation”), the displacement control valve is energized and controlled by the control computer, and the electromagnetic force generated by the solenoid pivots the valve body. , and the main valve is opened and closed to adjust the control pressure Pc in the control chamber of the variable displacement compressor.

During normal control of the displacement control valve, the pressure in the control chamber of the variable displacement compressor is appropriately controlled, and the stroke amount of the piston is changed by continuously changing the inclination angle of the swash plate with respect to the rotating shaft. The amount of fluid discharged into the discharge chamber is controlled by adjusting the air conditioning system so that the desired cooling capacity can be obtained. When the variable displacement compressor is driven at maximum displacement, the main valve of the displacement control valve is closed to lower the pressure in the control chamber, thereby maximizing the inclination angle of the swash plate. there is

In addition, an auxiliary communication passage is formed to communicate between the control port and the suction port of the displacement control valve, and at startup, the refrigerant in the control chamber of the variable displacement compressor flows through the control port, the auxiliary communication passage, and the suction port. It is also known that the responsiveness of a variable displacement compressor is improved by quickly reducing the pressure in the control chamber at the time of start-up so as to discharge air into the suction chamber of the compressor (see Patent Document 1). .

Japanese Patent No. 5167121 (page 7, FIG. 2)

However, in Patent Document 1, although the fluid discharge function is excellent at the time of start-up, when the variable capacity compressor is continuously driven, the auxiliary communication passage is in communication and the refrigerant flows from the control port to the suction port. The controllability of the pressure in the control chamber is poor, and there is a risk that the operating efficiency of the variable capacity compressor will be lowered.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a displacement control valve that has a fluid discharge function at the time of start-up and has good operational efficiency.

In order to solve the above problems, the displacement control valve of the present invention
A valve housing formed with a discharge port through which discharge fluid at discharge pressure passes, a suction port through which suction fluid at suction pressure passes, and a control port through which control fluid at control pressure passes, a rod driven by a solenoid, and a main valve a main valve configured by a seat and a main valve body and configured to open and close communication between the discharge port and the control port by movement of the rod, the displacement control valve comprising:
a CS valve that opens and closes communication between the control port and the suction port by movement of the rod;
biasing means for biasing the main valve body and the rod in directions opposite to each other;
The main valve body and the rod are arranged so as to be relatively movable in the axial direction.
According to this, since the main valve element is arranged so as to be able to move relative to the rod, the main valve can be controlled while the CS valve is closed. In addition, when the main valve is closed at startup and in the maximum energized state, the rod opens the CS valve to allow communication between the control port and the suction port, thereby maintaining the control pressure and the suction pressure at equal pressure (same pressure). can be done. On the other hand, when the main valve is controlled in the energized state, by closing the CS valve to block the control port and the intake port, it is possible to prevent the control fluid from flowing into the area into which the intake fluid is introduced. In this way, it is possible to increase the discharge of the liquid refrigerant and the operating efficiency when the variable displacement compressor is started.

The main valve body may have a locking portion against relative movement of the rod in the axial direction.
According to this, it is possible to accurately position the valve body in the axial direction with respect to the rod by the locking portion.

The CS valve may be of spool valve construction.
According to this, because of the spool valve structure, the CS valve is closed when the rod is axially stroked by a predetermined amount or more, and the CS valve can be reliably closed.

The main valve element and the rod may each be provided with an abutting portion that abuts on them in the axial direction.
According to this, the maximum opening degree of the CS valve can be adjusted.

The main valve body may have an inner periphery that slides on the rod and an outer periphery that slides on the valve housing.
According to this, the axial relative movement between the main valve body and the rod can be stabilized.

The rod may be provided with a spring receiving portion with which one end of the biasing means abuts.
According to this, the sliding structure of the main valve body with respect to the rod can be simplified.

A pressure-driven valve that opens and closes according to the suction pressure,
The rod may be formed with a hollow communication passage that allows communication between the control port and the suction port by opening and closing the pressure-driven valve.
According to this, since the refrigerant can be discharged also by the pressure-driven valve at the time of start-up, the refrigerant can be discharged quickly.

The control port may consist of a first control port and a second control port, and may be arranged in the order of the intake port, the second control port, the discharge port, and the first control port from the solenoid side.
According to this, since the intake port and the second control port are adjacent to each other, the displacement control valve having the CS valve has a simple structure.

1 is a schematic configuration diagram showing a swash plate type variable displacement compressor incorporating a displacement control valve according to an embodiment of the present invention; FIG. FIG. 4 is a cross-sectional view showing how the main valve is opened and the CS valve is closed when the displacement control valve of the embodiment is in a non-energized state; FIG. 3 is an enlarged cross-sectional view of FIG. 2 showing a state in which the main valve is opened and the CS valve is closed in the non-energized state of the capacity control valve of the embodiment; FIG. 5 is a cross-sectional view showing a state in which the main valve is closed and the CS valve is closed when the capacity control valve of the embodiment is energized (during normal control); FIG. 5 is an enlarged cross-sectional view of FIG. 4 showing a state in which the main valve is closed and the CS valve is closed in the energized state (during normal control) of the capacity control valve of the embodiment; FIG. 4 is a cross-sectional view showing a state in which the main valve is closed and the CS valve is opened during control in the energized state (starting) and the maximum energized state of the capacity control valve of the embodiment; FIG. 7 is an enlarged cross-sectional view of FIG. 6 showing how the main valve is closed and the CS valve is opened during control of the energized state (starting) and the maximum energized state of the displacement control valve of the embodiment; FIG. 11 is an enlarged cross-sectional view showing a state in which the main valve is opened and the CS valve is closed in the de-energized state of the displacement control valve of the modified example of the present embodiment;

A mode for carrying out the displacement control valve according to the present invention will be described below based on an embodiment.

A displacement control valve according to an embodiment will be described with reference to FIGS. 1 to 7. FIG. In the following description, the left and right sides of the capacity control valve are defined as viewed from the front side of FIG.

The displacement control valve V of the present invention is incorporated in a variable displacement compressor M used in an air conditioning system of an automobile or the like, and variably controls the pressure of a working fluid (hereinafter simply referred to as "fluid"), which is a refrigerant. By controlling the discharge amount of the variable capacity compressor M, the air conditioning system is adjusted to have a desired cooling capacity.

First, the variable capacity compressor M will be described. As shown in FIG. 1, a variable displacement compressor M has a casing 1 with a discharge chamber 2, a suction chamber 3, a control chamber 4, and a plurality of cylinders 4a. The variable capacity compressor M is provided with a communication passage (not shown) that directly communicates the control chamber 4 and the suction chamber 3, and the pressure of the suction chamber 3 and the control chamber 4 is balanced in this communication passage. A fixed orifice is provided for adjustment.

The variable capacity compressor M is eccentrically connected to a rotating shaft 5 installed outside the casing 1 and driven by an engine (not shown), and to the rotating shaft 5 in the control chamber 4 by a hinge mechanism 8. and a plurality of pistons 7 connected to the swash plate 6 and fitted reciprocally in each cylinder 4a. , the suction pressure Ps of the suction chamber 3 for sucking the fluid, the discharge pressure Pd of the discharge chamber 2 discharging the fluid pressurized by the piston 7, and the control pressure Pc of the control chamber 4 containing the swash plate 6, By appropriately controlling the pressure in the control chamber 4 to continuously change the inclination angle of the swash plate 6, the stroke amount of the piston 7 is changed to control the discharge amount of the fluid. For convenience of explanation, the illustration of the displacement control valve V incorporated in the displacement variable compressor M is omitted in FIG.

Specifically, the higher the control pressure Pc in the control chamber 4, the smaller the inclination angle of the swash plate 6 with respect to the rotary shaft 5 and the smaller the stroke of the piston 7. The swash plate 6 is substantially perpendicular to the shaft 5, that is, slightly inclined from the vertical. At this time, the stroke amount of the piston 7 is minimized, and the pressurization of the fluid in the cylinder 4a by the piston 7 is minimized. becomes. On the other hand, the lower the control pressure Pc in the control chamber 4, the greater the inclination angle of the swash plate 6 with respect to the rotating shaft 5, and the greater the stroke of the piston 7. , the swash plate 6 becomes the maximum inclination angle. At this time, the stroke amount of the piston 7 is maximized, and the pressurization of the fluid in the cylinder 4a by the piston 7 is maximized. becomes.

As shown in FIG. 2, the displacement control valve V incorporated in the displacement variable compressor M adjusts the current applied to the coil 86 constituting the solenoid 80 to , the CS valve 56 is controlled to open and close, and the pressure-sensitive body 61 is operated by the suction pressure Ps in the intermediate communication passage 57 as a hollow communication passage to control the opening and closing of the pressure-sensitive valve 53 as a pressure-driven valve. The control pressure Pc in the control chamber 4 is variably controlled by controlling the fluid flowing into the control chamber 4 or flowing out from the control chamber 4 .

In this embodiment, the main valve 50 is composed of a main valve body 51 and a main valve seat 10a formed on the inner peripheral surface of the valve housing 10, and the axial left end 51a of the main valve body 51 serves as the main valve seat. The main valve 50 is opened and closed by contacting and separating from 10a. The pressure-sensitive valve 53 is composed of a cap 70 forming a pressure-sensitive body 61 and a pressure-sensitive valve seat 52a formed at the axial left end of the pressure-sensitive valve member 52 as a rod. The pressure-sensitive valve 53 opens and closes when the sealing surface 70a formed on the side comes into contact with and separates from the pressure-sensitive valve seat 52a. The sub-valve 55 is composed of a sub-valve body 54 as a rod and a sub-valve seat 82a formed on the open end face of a fixed iron core 82, that is, on the left end face in the axial direction. The sub-valve 55 is opened and closed by contacting and separating from the sub-valve seat 82a. The CS valve 56 has a spool valve structure, and includes an annular convex portion 54c formed on the outer peripheral surface of the sub-valve element 54 and a CS valve seat formed on the inner peripheral surface of an annular ridge extending radially inward of the valve housing 10. 10c, and the CS valve 56 opens and closes when the annular projection 54c of the sub-valve 54 contacts and separates from the CS valve seat 10c.

Next, the structure of the capacity control valve V will be explained. As shown in FIG. 2, the capacity control valve V includes a valve housing 10 made of a metal material or a resin material, a main valve body 51 arranged in the valve housing 10 so as to be able to reciprocate in the axial direction, and a pressure sensing valve. A member 52 , a sub valve body 54 , a pressure sensing body 61 that imparts an axially rightward biasing force to the pressure sensing valve member 52 and the sub valve body 54 according to the suction pressure Ps in the intermediate communication passage 57 , and the valve housing 10 . , a pressure sensitive valve member 52, and a solenoid 80 that exerts a driving force on the sub-valve 54.

As shown in FIG. 2, the solenoid 80 includes a casing 81 having an opening 81a that opens axially to the left, and a solenoid 80 that is inserted into the opening 81a of the casing 81 from the left in the axial direction and extends to the inner diameter side of the casing 81. A substantially cylindrical fixed iron core 82 to be fixed, a drive rod 83 that is axially reciprocable on the inner diameter side of the fixed iron core 82, and whose axial left end is connected and fixed to the sub valve body 54, and the drive rod 83. a coil spring 85 provided between the fixed core 82 and the movable core 84 to bias the movable core 84 axially rightward; and an excitation coil 86 wound via a bobbin.

A recess 81b is formed in the casing 81 so that the inner diameter side of the left end in the axial direction is recessed to the right in the axial direction. there is

The fixed iron core 82 is formed of a rigid body that is a magnetic material such as iron or silicon steel. A sub-valve seat 82a is formed on the axially left end surface of the cylindrical portion 82b.

As shown in FIG. 2, the valve housing 10 includes a Pd port 12 as a discharge port that communicates with the discharge chamber 2 of the variable displacement compressor M, and a control valve that communicates with the control chamber 4 of the variable displacement compressor M. A first Pc port 13 as a port and a first control port, and a second Pc as a control port and a second control port that is adjacent to the right in the axial direction of the Pd port 12 and communicates with the control chamber 4 of the variable displacement compressor M. A port 14 and a Ps port 15 as a suction port communicating with the suction chamber 3 of the variable displacement compressor M are formed.

Further, the valve housing 10 has a substantially cylindrical shape with a bottom by press-fitting a partition adjusting member 11 into the left end portion in the axial direction in a substantially sealed manner. The partition adjustment member 11 can adjust the urging force of the pressure sensitive body 61 by adjusting the installation position in the axial direction of the valve housing 10 .

A main valve body 51 , a pressure sensing valve member 52 and a sub valve body 54 are arranged inside the valve housing 10 so as to reciprocate in the axial direction. A small-diameter guide surface 10b that can be slidably contacted in a substantially sealed state is formed on the outer peripheral surface of the valve, and a small-diameter CS valve seat 10c that allows the annular protrusion 54c of the sub-valve 54 to contact and separate is formed.

Inside the valve housing 10, a first valve chamber 20 communicates with the Pd port 12 and in which the axial left end 51a side of the main valve body 51 is arranged; The second valve chamber 30 in which the right end 51f side and the axial left end 54g side of the sub-valve element 54 are arranged, communicates with the first Pc port 13, and the pressure sensitive valve seat 52a side of the pressure sensitive valve member 52, that is, the axial left side is arranged. A pressure sensing chamber 60 and a third valve chamber 40 communicating with the Ps port 15 and in which the axial right end 54a side of the sub valve body 54 is arranged are formed. The second valve chamber 30 includes the outer peripheral surfaces of the main valve element 51 and the sub-valve element 54, and the inner peripheral surface on the axial right side of the guide surface 10b of the valve housing 10 and on the axial left side of the CS valve seat 10c. is defined by The third valve chamber 40 is defined by the outer peripheral surface of the sub-valve element 54, the axially left end surface of the fixed iron core 82, and the inner peripheral surface of the valve housing 10 axially rightward of the CS valve seat 10c. ing.

As shown in FIG. 2, the pressure sensitive body 61 is mainly composed of a bellows core 62 containing a coil spring 63 and a disk-shaped cap 70 provided at the right end of the bellows core 62 in the axial direction. The axial left end of the bellows core 62 is fixed to the partition adjusting member 11 .

The pressure sensing body 61 is arranged in the pressure sensing chamber 60, and the sealing surface 70a of the cap 70 is pushed to the pressure sensing valve member by the urging force of the coil spring 63 and the bellows core 62 that moves the cap 70 to the right in the axial direction. 52 is seated on a pressure sensitive valve seat 52a. Further, the cap 70 is applied with a force to move the cap 70 leftward in the axial direction according to the suction pressure Ps in the intermediate communication passage 57 .

As shown in FIG. 3, the main valve body 51 includes a mounting portion 51b to which the axial left end portion of a coil spring 91 as an urging means is fitted, and an axially left end of the mounting portion 51b extending in the outer diameter direction. A cylinder formed with an annular surface 51c and an axial left end 51a extending axially leftward from the outer diameter side of the annular surface 51c and having a larger diameter than the mounting portion 51b and contacting and separating from the main valve seat 10a of the valve housing 10. It is configured in a stepped cylindrical shape having a portion 51d. A minute gap is formed between the outer peripheral surface of the cylindrical portion 51d and the guide surface 10b of the valve housing 10 by separating it slightly in the radial direction. It is possible to move smoothly in the axial direction relative to each other.

The inner side of the main valve body 51 is on the side of the mounting portion 51b, that is, is configured in a stepped cylindrical shape with a larger inner diameter on the left side of the cylindrical portion 51d than on the right side in the axial direction. An annular surface 51e extending in the outer diameter direction from the axial left end of the inner peripheral surface of the mounting portion 51b and continuing perpendicularly to the surface 51c is formed substantially to the right of the surface 51c. That is, the attachment portion 51b is formed with a hook-shaped engaging portion 51g protruding radially to the right in the axial direction.

As shown in FIG. 3, the pressure sensing valve member 52 includes a cylindrical portion 52b to which the main valve body 51 is fitted, and a pressure sensing body 61 formed on the left side of the cylindrical portion 52b in the axial direction and having a diameter larger than that of the cylindrical portion 52b. and a contact portion 52c formed with a pressure-sensitive valve seat 52a that contacts and separates from the sealing surface 70a of the cap 70.

A fitting portion 52d having a diameter slightly smaller than that of the cylindrical portion 52b is formed at the axially right end portion of the cylindrical portion 52b of the pressure-sensitive valve member 52. is formed with an annular surface 52e extending to the . A small gap is formed between the inner peripheral surface of the engaging portion 51g of the main valve body 51 and the outer peripheral surface of the fitting portion 52d of the pressure sensing valve member 52 by separating them slightly in the radial direction. , the main valve body 51 and the pressure-sensitive valve member 52 can be smoothly moved relative to each other in the axial direction by sliding.

As shown in FIG. 3, the sub-valve element 54 includes a cylindrical portion 54b formed with an axially right end 54a, an annular convex portion 54c projecting radially outward from the axially left side of the cylindrical portion 54b, and an annular convex portion 54b. The mounting portion 54d is formed to have a diameter smaller than that of the cylindrical portion 54b. The outer diameter of the mounting portion 54d of the sub valve body 54 is substantially the same as the outer diameter of the mounting portion 51b of the main valve body 51. As shown in FIG.

A recess 54e is formed in the mounting portion 54d of the sub-valve 54 so that the inner diameter side of the left end in the axial direction is recessed to the right in the axial direction. As a result, the pressure sensitive valve member 52 and the sub valve body 54 are integrally connected and fixed. A drive rod 83 is connected and fixed to the axial right end of the sub-valve element 54, so that the pressure-sensitive valve member 52, the sub-valve element 54, and the drive rod 83 move together in the axial direction. there is Furthermore, an intermediate communication passage 57 is formed inside the pressure-sensitive valve member 52 and the sub-valve body 54 so as to penetrate in the axial direction by connecting the hollow holes. The intermediate communication passage 57 can communicate with the third valve chamber 40 via a communication hole 83a formed in the left end portion of the drive rod 83 in the axial direction. Although illustration is omitted for convenience of explanation, if the variable displacement compressor M is left in a stopped state for a long time, the fluid that has reached a high pressure in the control chamber 4 may liquefy. By starting the machine M and energizing the capacity control valve V, the main valve 50 is closed and the sub valve 55 is opened. By contracting and opening the pressure sensitive valve 53, the liquid refrigerant in the control chamber 4 can be discharged to the suction chamber 3 through the intermediate communication passage 57 in a short period of time.

Further, the annular convex portion 54c of the sub-valve element 54 reciprocates in the axial direction, thereby changing the amount of overlap with the CS valve seat 10c formed on the inner peripheral surface of the valve housing 10 when viewed in the radial direction. It constitutes a CS valve 56 that opens and closes communication between the control fluid that has passed through the 2Pc port 14 and the intake fluid that has passed through the Ps port 15 . The CS valve 56 is closed at a position where the annular protrusion 54c and the CS valve seat 10c overlap when viewed in the radial direction (see FIGS. 2 to 5). When the CS valve 56 is closed, the control fluid slightly leaks to the intake fluid side.

As shown in FIG. 3, the axial left end of the coil spring 91 contacts the annular surface 51c of the main valve body 51, and the axial right end of the coil spring 91 contacts the annular projection 54c of the sub valve body 54 in the axial direction. It is in contact with the side surface 54f as the left spring receiving portion. That is, the main valve body 51 , the pressure sensing valve member 52 and the sub valve body 54 are urged by the coil spring 91 in axially opposite directions. In addition, the coil spring 91 is a compression spring, and its outer periphery is separated from the inner peripheral surface of the valve housing 10 in the radial direction.

Further, the auxiliary valve body 54 is integrally connected and fixed to the fitting portion 52d of the pressure sensing valve member 52 while the main valve body 51 is fitted onto the cylindrical portion 52b and the fitting portion 52d of the pressure sensing valve member 52. An annular recessed groove 58 is formed. The groove 58 is formed by the outer peripheral surface of the fitting portion 52d of the pressure-sensitive valve member 52, the annular surface 52e of the pressure-sensitive valve member 52, and the axial left end 54g as a contact portion of the sub valve body 54. 58 regulates the axial position of the main valve body 51 with respect to the pressure-sensitive valve member 52 and the sub-valve body 54, and allows the main valve 50 to be opened in the non-energized state and to close the main valve 50 in the energized state. The opening degree of the valve 56 can be adjusted.

Specifically, in the energized state, the left axial end 51a of the main valve body 51 comes into contact with the main valve seat 10a, thereby closing the main valve 50 and opening the CS valve 56 by the annular projection 54c of the sub-valve body 54. In the state (see FIGS. 6 and 7), the axial left end 54g of the sub-valve element 54 forming the concave groove 58 abuts against the axial right end 51f of the main valve element 51 as the contact portion, thereby forming an annular shape. The axial positions of the pressure-sensitive valve member 52 and the sub-valve element 54 with respect to the main valve element 51 are determined by the convex portion 54c when the CS valve 56 is opened. That is, the opening degree of the CS valve 56 can be adjusted and the maximum opening degree can be determined.

Moreover, the difference between the axial dimension L58 of the groove 58 and the axial dimension L51g of the engaging portion 51g of the main valve body 51 is the axial right end 51f of the main valve body 51 and the axial left end 54g of the subvalve body 54. and the axial distance A (L58-L51g=A, see FIG. 3). That is, the main valve body 51 , the pressure sensing valve member 52 and the sub valve body 54 move axially leftward together to close the main valve 50 , and then the pressure sensing valve member 52 and the sub valve body 54 move relative to the main valve body 51 . Body 54 is further axially movable by a separation dimension A (see FIGS. 6 and 7).

Next, regarding the operation of the displacement control valve V and the operation of the opening/closing mechanism of the CS valve 56 by the axial movement of the main valve body 51, the pressure sensing valve member 52, and the sub-valve body 54, during normal control, during startup, and during control in the maximum energized state. will be explained in order.

First, normal control of the displacement control valve V will be described. During normal control, that is, during duty control, the displacement control valve V adjusts the opening degree and opening time of the main valve 50 to control the flow rate of fluid discharged from the Pd port 12 to the first Pc port 13 . At this time, the axially right side of the annular convex portion 54c of the sub-valve element 54 overlaps the axially left side of the CS valve seat 10c of the valve housing 10 as viewed in the radial direction, and the control fluid that has passed through the second Pc port 14 and the Ps port 15 are connected. The CS valve 56 maintains a state in which the communication with the inhaled fluid that has passed is closed. In this way, during normal control, the CS valve 56 is closed, so that the flow rate in the flow path connecting the second Pc port 14 and the Ps port 15 is throttled, and the control fluid that has passed through the second Pc port 14 reaches the Ps port 15 Therefore, the controllability of the control pressure Pc in the control chamber 4 is excellent, and the operating efficiency of the variable displacement compressor M can be improved (see FIGS. 4 and 5). In other words, the opening and closing of the main valve 50 can be controlled while the CS valve 56 is closed.

Next, the time of starting and the time of controlling the maximum energization state will be described. After the variable displacement compressor M is left unused for a long time, the discharge pressure Pd, the control pressure Pc, and the suction pressure Ps are substantially balanced. As shown in FIGS. 2 and 3, in the non-energized state, the displacement control valve V moves the pressure sensing valve member 52 and the auxiliary valve body 54 axially rightward by the biasing force of the coil spring 63 that constitutes the pressure sensing body 61 . As a result, the axial right end 54a of the sub-valve element 54 is seated on the sub-valve seat 82a of the fixed iron core 82 to close the sub-valve 55, and the axial left end 51a of the main valve element 51 moves toward the valve housing. A main valve 50 is opened while being separated from a main valve seat 10a formed on the inner peripheral surface of the valve 10 . At this time, the annular convex portion 54c of the sub-valve element 54 overlaps the CS valve seat 10c of the valve housing 10 when viewed in the radial direction, and communication between the control fluid that has passed through the second Pc port 14 and the intake fluid that has passed through the Ps port 15 is interrupted. It is closed by the CS valve 56 .

By starting the variable displacement compressor M and energizing the displacement control valve V, the main valve 50 is closed and the sub valve 55 is opened. At the time of start-up, the capacity control valve V is energized with the maximum duty, that is, in the maximum energized state. Since the body 54 moves further to the left in the axial direction by the separation dimension A (see FIG. 5), the CS valve 56 is opened and a flow path for discharging fluid from the second Pc port 14 to the Ps port 15 is formed. It is possible to discharge the liquefied fluid in the control chamber 4 in a short period of time and improve the responsiveness at the time of start-up.

When the displacement variable compressor M is driven at the maximum displacement, the main valve 50 is closed by energizing the displacement control valve V to the maximum duty, that is, the maximum energization state, as in the case of startup. At the same time, the CS valve 56 can be opened to allow communication between the second Pc port 14 and the Ps port 15, so that the control pressure Pc can be sufficiently lowered and the control pressure Pc and the suction pressure Ps can be equalized (same pressure). Easy to keep in good condition. Therefore, it is possible to stabilize the stroke of the piston 7 in the cylinder 4a of the control chamber 4, maintain the maximum displacement state, and improve the operating efficiency.

Further, the main valve body 51 is configured such that the annular surface 51e of the locking portion 51g is engaged with the annular surface 52e of the pressure sensitive valve member 52, so that the axial direction of the main valve body 51 with respect to the pressure sensitive valve member 52 and the sub valve body 54 is adjusted. Positioning can be performed accurately. Furthermore, the mounting accuracy of the main valve body 51 with respect to the pressure sensitive valve member 52 can be improved.

In addition, since the CS valve 56 is configured in a spool valve structure by the annular projection 54c of the sub-valve element 54 and the CS valve seat 10c formed on the inner peripheral surface of the valve housing 10, the pressure-sensitive valve member 52 and the sub-valve When the body 54 is axially stroked by a predetermined amount or more, the CS valve 56 is closed, and the CS valve 56 can be reliably closed. Furthermore, for example, during normal control, even if the pressure sensing valve member 52 and the sub-valve element 54 move slightly in the axial direction due to disturbance such as vibration, the CS valve 56 is maintained in a closed state. , tolerant to disturbances and excellent in control accuracy.

In the main valve body 51, the inner peripheral surface of the engaging portion 51g and the outer peripheral surface of the fitting portion 52d of the pressure sensitive valve member 52 slide against the pressure sensitive valve member 52, and the outer peripheral surface of the cylindrical portion 51d and the valve housing are closed. Since the guide surface 10b of 10 slides, the axial relative movement between the main valve body 51 and the pressure-sensitive valve member 52 and the sub-valve body 54 can be stabilized.

Further, since the sub-valve element 54 is provided with the axially left side surface 54f of the annular projection 54c against which the axially right end of the coil spring 91 abuts, the main valve element 51, the pressure sensing valve member 52, and the sub-valve element The slide structure with 54 can be simplified.

The main valve body 51, the pressure sensing valve member 52 and the sub valve body 54 are separate bodies, and the main valve body 51, the pressure sensing valve member 52 and the sub valve body 54 are separated by the axial left end 54g of the sub valve body 54. Since relative movement in the axial direction is restricted, the sliding structure of the main valve body 51, the pressure sensing valve member 52 and the sub valve body 54 can be simplified.

The valve housing 10 also has a first Pc port 13 arranged in the pressure sensing chamber 60 corresponding to the pressure sensing valve 53 and a second Pc port 14 arranged in the second valve chamber 30 corresponding to the CS valve 56 . By forming it, there is no need to form a flow path for circulating the control fluid inside the valve housing 10, and the structure can be simplified.

When the suction pressure Ps becomes high due to an abnormality or the like, the sub valve body 54 is pushed leftward by the suction pressure Ps to open the CS valve 56 and release the high suction pressure from the second Pc port 14. It is possible to do so.

Also, an example in which the CS valve 56 is configured by the annular projection 54c of the sub-valve element 54 and the CS valve seat 10c on the inner peripheral surface of the annular ridge of the valve housing 10 has been described, but as shown in FIG. The inner peripheral surface of the valve housing 10 is used as the CS valve seat 110c without providing a protrusion on the inner peripheral surface of the valve housing 10, and the annular projection 154c of the sub-valve element 54 is arranged so as to partially overlap the second Pc port 14 when viewed in the radial direction. You may By doing so, the valve housing 10 can be easily manufactured, and the sub-valve element 54 is tilted by tilting load or the like so that the annular projection 154c of the sub-valve element 54 and the annular ridge of the valve housing 10 are engaged. Not at all.

Although the embodiments of the present invention have been described above with reference to the drawings, the specific configuration is not limited to these embodiments, and any changes or additions within the scope of the present invention are included in the present invention. be

For example, in the above embodiment, the passage from the second Pc port 14 to the Ps port 15 is throttled by closing the CS valve 56, but this is not the only option, and the CS valve 56 is closed. Thus, the diameters of the annular projection 54c of the sub-valve element 54 and the CS valve seat 10c of the valve housing 10 may be set so that the passage from the second Pc port 14 to the Ps port 15 can be substantially blocked. .

Further, although the example in which the pressure sensitive valve member 52 and the sub valve body 54 are separately configured has been described, both may be formed integrally.

Further, the communication passage and the fixed orifice that directly communicate the control chamber 4 and the suction chamber 3 of the variable displacement compressor M may not be provided.

Further, in the above-described embodiment, the auxiliary valve may not be provided, and the axial right end of the auxiliary valve body may function as a support member for receiving an axial load, and the sealing function is not necessarily required.

Moreover, the coil spring 91 is not limited to a compression spring, and may be a tension spring or a shape other than a coil.

In addition, although the CS valve 56 is configured by the valve housing 10 and the sub-valve element 54 itself, the CS valve 56 may be configured by attaching separate members to the valve housing 10 and the sub-valve element 54 .

Also, the pressure sensitive body 61 may be one that does not use a coil spring inside.

Reference Signs List 1 casing 2 discharge chamber 3 suction chamber 4 control chamber 10 valve housing 10a main valve seat 10b guide surface 10c CS valve seat 11 partition adjustment member 12 Pd port (discharge port)
13 1st Pc port (control port, 1st control port)
14 Second Pc port (control port, second control port)
15 Ps port (intake port)
20 First valve chamber 30 Second valve chamber 40 Third valve chamber 50 Main valve 51 Main valve body 51a Axial left end 51b Mounting portion 51c Annular surface 51d Cylindrical portion 51e Annular surface 51f Axial right end (contact portion)
51g locking portion 52 pressure sensitive valve member (rod)
52a Pressure-sensitive valve seat 52b Cylindrical portion 52c Contact portion 52d Fitting portion 52e Annular surface 53 Pressure-sensitive valve (pressure-driven valve)
54 Auxiliary valve body (rod)
54a axial right end 54b cylindrical portion 54c annular convex portion 54d mounting portion 54e concave portion 54f side surface (spring receiving portion)
54g Axial left end (contact portion)
55 Auxiliary valve 56 CS valve 57 Intermediate communicating passage (hollow communicating passage)
58 concave groove 60 pressure sensing chamber 61 pressure sensing body 62 bellows core 63 coil spring 70 cap 70a sealing surface 80 solenoid 82 fixed iron core 82a sub valve seat 83 drive rod 91 coil spring (biasing means)
Pc Control pressure Pd Discharge pressure Ps Suction pressure V Displacement control valve

Claims (7)

A valve housing formed with a discharge port through which discharge fluid at discharge pressure passes, a suction port through which suction fluid at suction pressure passes, and a control port through which control fluid at control pressure passes, a rod driven by a solenoid, and a main valve a main valve configured by a seat and a main valve body and configured to open and close communication between the discharge port and the control port by movement of the rod, the displacement control valve comprising:
a CS valve that opens and closes communication between the control port and the suction port by movement of the rod;
biasing means for biasing the main valve body and the rod in directions opposite to each other;
The main valve body and the rod are arranged so as to be relatively movable in the axial direction,
A pressure-driven valve that opens and closes according to the suction pressure,
A displacement control valve, wherein the rod is formed with a hollow communication passage that allows communication between the control port and the suction port by opening and closing the pressure-driven valve. 2. The displacement control valve according to claim 1, wherein the main valve element has a locking portion against relative movement of the rod in the axial direction. 3. The displacement control valve according to claim 1, wherein the CS valve is of spool valve construction. 4. The capacity control valve according to any one of claims 1 to 3, wherein the main valve body and the rod are each provided with an abutting portion that abuts axially. 5. The displacement control valve according to claim 1, wherein the main valve body has an inner periphery that slides on the rod and an outer periphery that slides on the valve housing. 6. The displacement control valve according to any one of claims 1 to 5, wherein the rod is provided with a spring receiving portion with which one end of the biasing means abuts. 3. The control port is composed of a first control port and a second control port, and the intake port, the second control port, the discharge port, and the first control port are arranged in this order from the solenoid side. 7. The capacity control valve according to any one of 6 .

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